Grinding machine



May 26, 1942. J. I. GARSIDE GRINDING MACHINE Filed June 19, 1940 4 Sheets-Sheet 1 2.1mm JUHN 1T EF/F? 5/05 -May 26, 1942. J. L GARSIDE GRINDING MACHINE Filed June 19, 1940' 4 Sheets-Sheet 2 E E o:

Film

WE m m5 M. J

May 26, 1942.

GRINDING MACHINE Filed June 19, 1940 4 sheets-sheds I P 25 (ll i 36] 146, as $2 1 I56 I I13 i "z JOHN 5'HR5/0E J. I. GARSIDE 2,284,050

y 2- J. l. GARSIDE 2,284,050

' GRINDING MACHINE Filed June 19, 1940 4 Sheets-Sheet 4 JaH/v fEfiRs/aE Patented May-26, 1942 GRINDING MACHINE John I. Garside, West'Boylston, Masa, assignor to Norton Company, Worcester, Mass, a corporation of Massachusetts Application June 19, 1940, Serial No. 341,333

8. Claims.

The invention relates to grinding machines,

and more particularly to a hydraulically oper-.

ated multi-purpose grinding machine.

One object of the invention. is to provide a simple and thoroughly practical improved universal or multi-purpose grinding machine. Another object of the invention is to provide a multi-purpose grinding machine in which the wheel head may be angularly'adjusted and fed in a direction normal to the axis of the Work piece or in which the wheel slide support may be angularly adjusted so that the grinding Wheel may be fed in a direction at an angleto a planenormal to the work. axis. A further object of the invention is to provide an' improved multi-speed manually operable wheel feeding mechanism. Another object of the invention is. to provide an improved multi-speed manually operable traversing mechanism for traversing, thework supporting table longitudinally. Other objects will be in part obvious or. in part pointed out hereinafter.

The invention accordingly consists inzthe features. of construction, combinations of elements, and ararngements of parts; as will be exemplified in the structure to be hereinafter described, and the scope of the application of whichwill beindicated in the following claims.

In the accompanying drawings, in which is shown one of various possible: embodiments of the mechanical features of this invention:

Fig. 1 is a front elevation of the improved grinding machine; I

Fig. 2 is a right-hand end elevation, on: an

enlarged scale, of the grinding machine shownin Fig. 1, having parts broken away and shown in section to more cle'arly'show'the wheel feeding mechanism;

' Fig. 3 is a, fragmentary sectional view,.on an enlarged scale takenv approximately on the line 33 of Fig. 2,. showingthe wheel slide supporting and adjusting mechanism;

Fig. 4 is a fragmentary sectional view, on an enlarged scale, taken approximately on theline 44 of Fig. 1;

Fig. 5 is a fragmentary cross sectional view, on L an enlarged scale, taken approximately on the line 5-5 of Fig. 1, showing the manually operable table traversemechanism;

Fig. 6 is a fragmentary sectional view. taken approximately on the line 6- 6 of Fig. 5;

Fig. 7 is a'fragmentary view, showing the man-- ually operable change gear mechanism for the wheel feeding mechanism; and v Fig. 8 is a fragmentary cross-sectional view,

on an enlargedv scale, taken approximately on the line 8,8 of Fig.4.

As illustrated in the drawings, a grindingmachine isprovided having a base I0. which supports; a longitudinally reciprooable work supporting table. on the usual flat way I2 and V- way l3 for a longitudinal reciprocatory movement relative to the base I 0.

A rotatable work support is provided for the table I I comprising a headstock l4 and a footstock l5 which are provided with work supporting centers 16' and I1, respectively. The headstock 14 is preferablyamotor driven headstock having an electric motor 18 mounted on the upper surfaceof the headstock [4. The motor is provided with a'multi-v-groovedpulley l9 which is connected by multiple V-belts 20"with a pulley 2| which may be mounted on the left-hand end of a headstock spindle 22;

A rotatable grinding wheel 25 is supported on the left-hand end of a Wheel spindle 26 (Fig. 1). The wheel spindle 26 is rotatably supported'in suitable bearings (not shown) in a wheel head 21. A driving mechanism is provided forrotating the grinding wheel 25comprisingan electric motor 28 having a driving pulley 23 which is connected by multiple V -belts30 with a pulley 3| mounted on the'right-hand end of the wheel spindle 26 (Fig. 1-).-The motor 28 is preferably mounted on a motor support 32 which is pivotally supported on a shaft 33 mounted on the rear end of the wheel head" 27-. The pivotal mount for the motor provides means whereby the driving belt 38 may be tensioned as desired.

The wheelhead 21- is supported on a'trans versely movable wheel slide 35. The wheel slide 35 is supported for-a transverse movement on a V-way 36 and a flat way 31 formed between the wheel slide 35 and a wheel slide base 38. In or-,- der to provide a swivel adjustment for the wheel spindle relative to the slide, a swivel adjustment is provided between the wheel head 21 and the wheel slide 35. The wheel head 27 is provided with an enlarged circular base portion 40 which is provided with adownwardly projecting annular shaped projection 4| which mates with a correspondingly shaped aperture 42 formed in the upper surface of a transversely adjustable member 42a. The member 42a is transverselyadjustable on the upper surface of the wheel slide 35. A binder bolt 43 has its enlarged-head 44 held in a T-shaped slot 45 formed inthe upper portion of the wheel slide 35., The binder bolt 43 passes through a central aperture 46 in the wheel headimember 21 and a cen r l ap u e I 2,284,050 7 r a The speed reduction unit 13 may be any of the well known speed reducing units. The unit illustrated, however, is the well known heliocentric speed reduction unit manufactured by the Universal Gear Corporation of Indianapolis,

Indiana. The heliocentric unit 13 is rotatably supported in bearings 14 and 15 which are carried byanapron 16., The driven or input shaft 12 of the heliocentric unit13 carries a pair of eccentrics 62 and 62a. A rotatable output or driven shaft TI is fixedly mounted to a on the wheel slide 35. The periphery of the en- 4 larged portion 48 of the grinding wheel head 21 and its supporting portion of the wheel slide 35 may be graduated, if desired, so that the 'grinding wheel head 21 may be angularly adjusted for a grinding operation when desired. This adto the work axis so that a tapered portion of the work piece maybe ground -with a true cylindrical face on the grinding wheel. When the binder bolt-43 is loosened to facilitate arijangular adjustment. of the wheel head; 21;,"a rapid transverse positioningmovement of the wheel head 21 may be obtainedby sliding thewheel head 21 together with its supporting member 42a transversely on the wheel slide 35 to pos tion the gr nding wheel 25in setting 'up the machine,

the binder-bolt 43 may be looked after which toclamp the parts in adjustedposition.

In certain types ofgrinding, it is desirable to provide an angular adjustment for the wheel slide so that instead of traveling transversely in a path normal to the work axis, it may be moved transversely in a path at an angle thereto. To

accomplish this result, thewheel slide base 38 is provided with a downwardly projecting flange 52 which .mates with 1a cylindrical surface 53 formed on a plate 54 which is fixedly mounted onthe rear portionof the base Ill. The plate 54 is provided with acir'cular shaped T-slot '55. Clamping screws'56 and 51 are provided with enlarged heads which slidein the T-slot 55 and pass throughapertures'58 and59 formedin the wheelslide base 38 ,on diametrically opposite sides thereof! It will befreadily apparent from the foregoing disclosure" that by loosening anut 68 and a nut 6|; the wheel slide base 38 may be rotated to' positio'n the V-way 36 and flat way 31 at an angle other than normalto the work axis. The peripheral surface 53 may, if desired,

be graduatedso that thelpos ition of the V-way,

36 and flat way 31 of thewheel slide base 38 may be adjusted to'thedesired angular position, after which th nuts"60 and 6! may again be clamped to'lockthe wheel slide'ba'se 38 in adjusted position. It'will v the foregoing disclosurethatthe wheel slidebase 38 may be adjusted in either direction and through -360, if-desired. Y

l Manually operabletqble traverse A-manually operable table traverse mechanism is; provided, preferably of fa multi-spee'd type, whereby the table ll maybe traversed manually at acomparatively rapid rateto position the table and 'a workpiecesupported thereon relative to the grinding wheel 25, or may be traversedfat a relatively'slow rate of speed during a grind jg wheel truing operation. This mechamen may comprise a manually operable hand wheel'Hl which is provided withan enlarged hub illfl rhe and wheel hub 1| is slidablykeyed to'an input shaft I2 of a speed reduction unit 13.

justment is utilized where it is desired to adjust the position of the wheel axis angularly relative v be readilyapparent from 7 supporting table I I.

to the casing, having the appearance of an internal ring gear, but with definitely differing tooth shapes, the teeth of the racks 64 and 64a being substantially wedge-shaped. Due to the working contact between the -arrow-pointed plungers 65 and 65a and the teeth of theracks 64 and64a, respectively, a combination sliding and rolling wedge action is obtained, forcing rotation with a minimum friction to the plunger holder 63 and the output or driven shaft 11. The input eccentrics 62 and 62a force the plungers out under load. Apair of retracting rings 66 and 66a ride in notches formed within the plungers 65 and 65a, respectively, to hold back on the no-load part of the cycle of operation.

A single setof plungers and stationary racks may be employed, but for the maximum smoothness of operation andbalance of the working parts, a universal heliocentric reducer is employed, having two eccentrics 62 and 62a, as illustrated, each of which actuates a set of plungers 65 and 65a, respectively, in'operativeengagement with a pair of stationary racks 64 and 64a, respectively. Each set of plungers 65 and 65a is timed directly opposite or 180 degrees apart and has a carrying arc of approximately 120 degrees. The total'effect is a balanced distribution of power over two-thirds of the complete cycle so that a balanced and uniform 'slow rotation of the output or driven shaft 11 is transmitted to rotate the gear 86 and thereby transmit a traversing movement to the rack 81 and table I l.

The heliocentricunit 13 is rotatably supported in bearings 14 and 15 which are'carried by an a gear 18 which meshes with a rotatable idler gear 19 which is rotatably supported on a shaft 88 (Fig. 6). The gear 19 meshes with a gear 8| which is keyed on a rotatable shaft 82. .The shaft 82 is journalled in bearings 83 and 84 which are supported in a bracket 85 fixedly mounted on the apron 16. The shaft 82 rotatably supports a gear 86 which meshes with a rack bar 81 depending fromtheunder side of the work The shaft 82 also supports a clutch member 88 which is slidably keyed thereon and which is arranged to be moved into and out of meshwith clutch teeth89 formed integral with the'gear 86. When the clutch 88 is disengaged from the clutch teeth 89, no rotary motion may be transmitted between the shaft 88 and the gear 86.

is preferably divided'into two parts, namely, the

It. is desirable that during the hydraulic traverse of the table II, the hand traverse mechanism be rendered inoperative. In order to accomplish this result, a hydraulically operated mechanism is provided comprising a, cylinder 98. having a slidably mounted piston 9I therein which is arranged to engage and actuate a rock arm 92. The rock arm 92 is pivotally supported by a stud 93 which is in turn fixedly supported on the bracket 85. The upper end of the arm 92 is yoke-shaped and is provided with spaced diametrically opposed studs 94 which ride in a groove 95 formed in the periphery of the clutch member 88. A spring 96 is interposed between the lower end of the rock arm 92 and a depending projection 91 formed integral with the cylinder 98, normally tendin to hold the clutch member 88 in engagement with the clutch teeth 89 so that a hand traverse of the work supporting table H may be obtained by rotation of the hand wheel I8. The admission of fluid under pressure to the cylinder 98 servesto disengage the clutch member 88.

A clutch mechanism i provided between the hand wheel 'I8 and the unit 73, comprising an internal ring gear 98 which is fixedly mounted to the hub II to rotate with the hand wheel I8. A gear 99 of the same pitch diameter as the gear 98 is fixedly mounted to the heliocentric casing I3. When the hand wheel I8 is in the position illustrated in Fig. 5, the gear 98 meshes with the gear 99, operatively connecting the hand wheel I8 with the housing 13' of the heliocentric unit I3 so that when a rotary motion is imparted to the hand wheel I8, it will rotate the heliocentric unit and transmit a one to one rotation between the hand wheel I8 and the gear I8 which in turn transmits rotation through the clutch members 98-89 to rotate the gear 86 and thus impart a longitudinal traversing movement to the rack bar 8'! and the work supporting table II.

If a slow .traversing movement of the table II is desired, the hand wheel I is moved toward the left (Fig. 5) to disengage the ring gear '99 from the gear 99. A hinder or clamping screw 89 is tightened to lock theheliocentric casing I3 relative to the apron 76. In this position of the parts, any rotation of the hand wheel I8 is transmitted through the input shaft 12 which operates through the speed reduction unit to impart a slow rotary motion to the output shaft 11. The output shaft II in turn transmits arotary motion through the gear mechanism above described to the clutch parts 88 and 89 torotate the gear 88 and transmit a slow traversing movement to the rack bar 81 and the work supporting table II.

Grinding wheel feeding mechanism A grinding wheel feeding mechanism is provided for feeding the grinding Wheel slide 35 together with the grinding wheel 25 transversely toward and from the work axis. This mechanism may comprise a half nut I88 depending from the under side of the slide 35. The half nut I88 meshes with a rotatable cross feed screw I8I which is rotatably journalled in bearings I82 and I83 in the wheel slide base 38. Adjusting screws I84 and I85 are provided whereby the end thrust of the feed screw I III may be taken up. A bevel gear IDS is keyed on thereduced end portion of the feed screw "II. The bevel gear I86 meshes with a bevel gear I81 which iskeyed on the upper end of a rotatable shaft I88. The shaft I88 is journalled in a bearing I89 which is arranged so that the axis of the shaft I88 coincides with the axis of adjustment of the wheel slide base 38.

the gear I22.

' link I31.

A bevel gear H0 is fixedly mounted on the lower endof the shaft I88. The bevel gear II8 meshes with a bevel gear I I I which is keyed on the rear end of a rotatable shaft I I 2.

(Fig. 2). The shaft II2 supports a cluster gear I28 comprising a large diameter gear I2I and a smaller diameter gear I22 which mesh with a gear I23 and a gear I24,'respectively, supported on an output shaft I25 of a speed reduction unit to be hereinafter described. The gear I23 is rotatably supported on a reduced end portion of the shaft I 25 and is provided with clutch teeth I26 which are arranged to be engaged by clutch The clutch teeth I2I are formed integral with a slidably mounted clutch member I28 which is slidably keyed to the shaft I25. The gear I24 is formed integral with the clutch member I28. In the position of the parts as illustrated in Fig. 4, a rotary motion of the shaft I25 will be transmitted through the gear I24 to the gear I22 to rotate the shaft H2 and thus transmit a comparatively fast rotation to the feed screw IM to advance the grinding wheel either toward or from the work support, depending upon the direction of rotation of the hand wheel I45.

If it is desired to rotate the feed screw II at a slow speed, the clutch member I28 is moved toward the right (Fig. 4) so that the clutch teeth I21 engage the clutch teeth I26. During this movement, the gear I24 slides out of mesh with In this position of the parts, rotation of the shaft through the clutch member I28,'the clutch teeth I21, the clutch teeth I26, to impart a rotary motion to the gear I23 to rotate the gear I2I and, through the mechanism previously described, to rotate the feed screw IIJI at a comparatively slow rate of speed.

A manually operable mechanism is provided for actuating the clutch member I 28 from the operators control station in front of the machine. The clutch member I28 is provided with a groove A lever I38 is pivotally mounted on a stud I3I which is in turn fixedly supported by a-bracket I32 formed integral with an apron I33. The right-hand end of thelever I38 (Fig. 7) is yokeshaped and is provided with diametrically opposed shoes I34 and I35 which are positioned on diametrically opposite sides of the clutch member I 28 and which ride within the groove I29 formed thereon. The left-hand end of the lever I38 (Fig. 7) is connected by a stud I36 with a The link I3! is inv turn connected by a stud I38 with a slidably mounted shaft I39. The shaft I 39 slides longitudinally within a bearing surface I48 formed within the apron I33. A manually operable actuating knob MI is fixedly mounted on the outer end of the shaft I39 and projects from the front of the machine base. It will be readily apparent from the foregoing disclosure that .a downward movement of the knob I4I (Fig. 7) will rock the lever I38 in a counterclockwise direction so as to throw the gear I 24 out of mesh with the gear I22 and at the same time'throw the clutch teeth I2'I into engagement with the clutch teeth' I26' when it is desired to impart. a slow rotary movement to the feed screw IOI as above described.

In order to provide a relativelyslow rotation of the output shaft I25, a manually operable hand wheel I is provided. The hand Wheel I45 is connected in a manner to be hereinafter described The shaft II 2 is 1 journalled in bearings H3, H4, H5, H8 and II! I25 will be transmitted approximately 120 degrees.

v to aninput shaft I46 of a heliocentric speed'r'e ducing unit I41 (Fig.4). The speed reduction unit I41 is the well known heliocentric speed reduction unit similar in construction to the one previously described in connection with the table traversing mechanism. The driven or input shaft shapes, the teethof the racks ll and I52 being substantially wedge-shaped. Due to the working contact of the'sets of arrow-pointed plungers I53 and I54 and the teeth of the racks I5I and I52, respectively, a, combination sliding and rolling wedge action is obtained, forcing rotation with a minimum friction to the plunger holder I50 and the output or, driven shaft I25. The inputeccentrics I48 and I49 force the plungers I53 and I54 out under load. A pair of retracting rings I55 and I56 ride in notches formed within the side faces of the plungers I53 and I54, respectively, to hold them back on the no load part of their cycle of operation. 7

A single heliocentric unit or set of plungers and stationary racks may be employed, but for a maximum smoothness of operation and balance of the working parts, a universal heliocentric reducer is employed, having the two eccentrics I48 and I49 as illustrated and described above, each of which actuates a set of plungers I53 and I54, respectively, and in operative engagement with a pair of stationary racks I5I and I52, respectively.

Each set of plungers is timed directlyopposite or 180 degrees apart and has a carrying arc of The total efiect is a balanced distribution of power over twothirds of the complete cycle so that a balanced and uniform slow rotation of the output or driven shaft I is transmitted to rotate the feed screw IOI through the gear mechanism above described.

The heliocentric unit I41 is rotatably supported in bearings I51 and I58 in an apron I59. A binder screw I60 is provided for locking the unit I41 against rotation. A gear I6I is fixedly mounted to the hub portion I62 projecting from the unit I41. The manually operable feed Wheel I45 is supported on the hub I62 and is arranged to be connectedwith the input shaft I46 of the unit I41 by means of an index mechanism to be hereinafter described. An arm I63 is keyed to the input shaft I46. The arm I63 carries a spring-pressed index plunger I64 which is arranged to engage one of a series of holes I65 formed in a circular path on the front face of the hand wheel I45. A knob I66 is provided for retracting. the plunger I64 when desired to adjust the position of the shaft I46 relative to the hand wheel I45.

A clutch mechanism is provided between the hand wheel- I45 and the input shaft I46 so that the hand wheel maybe readily reset when desired. A gear I61 is fixedly mounted on the hand wheel I45. The gear I61 is an internal gear of the same pitch diameter as the gear I6I. The hand wheel I45 is normallyheld in the position illustrated in Fig. 4 by means of a plurality of symmetrically arranged, spring pressed plungers I68 (only one of which is shown in Fig. 4) These plungers serve normallyto. maintain the hand gear I61 meshing withthe'gear SI and thespring-pressed plungeri I64 engaging one of the index holes in the hand wheel I45. When it is desired to reset the hand wheel, it is moved toward the right (Fig. 4) on the hub I62 of the unit I41 against the compression of the plungers I68. This movement disengages the gear I 61 from the gear I6I so that the hand wheelmay be rotated to transmit a rotary motion to'the input shaft I46'while the housing I41 of the heliocentric unit is held stationary so as to impart a relatively slow rotation to the shaft I25 and thereby transmit a correspondingly slow rotary motion to the feed screw IOI.

A stop mechanism is provided comprising a stop abutment I10 which is pivotally supported by a stud "I on the apron I59; When desired, the stop abutment I10 may be rotated in a clockwise direction into an inoperative position so that the wheel I45 may be-rotated continuously without interference of the abutment. The hand wheel I45 supports a rotatablestop pin I12 having an enlarged head I13 half of which is slabbed off on one side so as to provide a semi-cylindrical stop surface I15 (Figs. 4 and 8) When the hand wheel I45 ls rotated-in a counterclockwise direction to produce an infeeding movement of the grinding wheel, the slabbed-ofi semi-cylindrical surface I15 moves into engagement with the stop abutment I10 (Fig. 8), thus positively limiting the rotation of the hand wheel I45 to stop the forward feeding movement of the grinding wheel slide 21 and the grinding wheel 25. When the hand wheel is rotated in a clockwise direction to produce a rearward movement of the slide 21 and the grinding wheel'25, the slabbed-off surface I14 of the stud I12 moves into position I14a (Fig. 8) whereupon continued movement produces a camming action between the slabbed-off surface I14 and the side face of the stop abutment I10 so as to rock the stop abutment I10 to an inoperative position and thus facilitate rotation of the hand wheel I45 to the desired extent. This enables the removal of the grinding wheel to a rearmost position as determined by the operator. After the ground piece of work has been removed from the machine and a new piece of work placed thereinstead, the hand wheel I45 may then be rotated in a counterclockwise direction to advance the wheel slide 21 and grinding wheel 25 toward the peripheral surface of the work piece. When the grinding wheel isin close proximity to the peripheral surface of the work piece, the

stop abutment I10 is then swung in a counterclockwise direction into the position, illustrated in Fig. 4 so that on the last rotation of the hand wheel, the semi-cylindrical stop surface I15 will be in the path of the stop abutment I10 to limit the infeeding movement of the grinding wheel.

In case it is desired to compensate for wheel wear, the feed wheel may be rotated until the semi-cylindrical surface I14 engages the stop abutment I10, after which the plunger I64 may be moved toward the left (Fig. 4) to disengage it from the hole I65, after which the arm I63 may berotated in the desired direction one or more holes to reset the position of the grinding wheel relative to the stop abutment and thus compensate for wear on the wheel due to the grinding operation. This adjustment is also useful during a grinding wheel truing operation and serves as afeeding mechanism whereby the grinding wheel 25 and it supporting slide 35 may be advanced by the desired and truing operation. a

The operation of the improved grinding mapredetermined amount for a chine will be readily apparent from the forework to be ground, that is,'with the grinding wheel axis parallel to the axis of the work piece so that a feeding movement may be had in a path normal to the work axis. The wheel head may be adjusted angularly to present *atruefcylindrical face for the grinding of a frusto-conica-l surface on the work piece or, if desired, the wheel slide base may be angularly adjusted so that a feeding movement may be obtained which is at an angle to a path normal to the work axis. The work table II may then be traversed longitudinally by rotation of the manually operable hand wheel either at a fast or a slow rate under manual power or may be traversed or reciprocated longitudinally by power as desired.

The grinding wheel may then be fed transversely either at a fast or a slow rate of feed by rotation of the manually operable feed wheel I45.

vided by this invention apparatus in which the various objects hereinabove set forth together with many thoroughly practical advantages are successfully achieved. As many possible embodiments may be made of the above invention and as many changes might be made in the embodiment above set forth, it is to be understood that all matter hereinbefore set forth or shown in the accompanying drawings is. to be interpreted as illustrative and not in a limiting sense.

I claim:

1. In a grinding machine having a base, a longitudinally movable rotatable work support and a transversely movable rotatable grinding wheel, a transversely movable wheel slide on said base, a transversely movable supporting member on said slide, an angularly adjustable head on said member to support said grinding wheel, said angularly adjustable wheel headand supporting member servingto facilitate a rapid It will thus be seen that there has been pro- I transverse and angular movement of the wheel head and grinding wheel relative to said slide, means to clamp said head and member in adjusted position, a swivel adjustment between said slide and said base whereby said.slide may be angularly positioned relative to the base, and

a wheel feeding mechanism operatively connected to move said slide transversely in any adjusted position thereof.

2. In a grinding machine having a base, a longitudinally movable rotatable work support and a transversely movable rotatable grinding wheel, a transversely movable wheel slide on said base,

-3...In a grinding machine having a base, a longitudinally movable rotatable work support and a 'transversely'movable rotatable grinding wheel, a transversely-movable wheelslide on said base, a transversely movable supporting member on said slide, an angularly adjustable wheel head on said member to supportsaid grinding wheel, said angularly adjustable wheelhead and supporting member serving to facilitate a rapid angular and transverse adjustment of the grinding wheel, means to clamp said head and supporting member in adjusted position on said slide, a swivel adjustment interposed between said slide and said basewhereby the slide may be angularly adjusted relative to the base, a nut and'screW feeding mechanism, and a manually operable feeding mechanism on the base, driving connections between said feeding mechanism and the feed screw comprising. a rotatable shaft which coincides with the axis of said swivel adjustment whereby the wheel slide may be adjusted transversely in any angular position of said slide.

4. In a grinding machine having a base, a transversely movable wheel slide on said base, a transversely movable supporting member on said slide, a rotatable grinding wheel, an angularly adjustable wheel head on said member to support said grinding wheel, means to clamp said head and supporting member in adjusted position on the slide, a swivel support interposed between the wheel slide and base, and a wheel feeding mechanism-for said slide comprising a nut and screw mechanism to move said slide, a rotatable shaft positioned to coincide with the axis of v the slide swivel adjustment, gearing connecting said shaft with said screw, and a manually operable feed mechanism on the base to rotate said shaft and thereby feed said grinding wheel transversely in any adjusted position of the wheel headand wheelslide.

5. In a grinding machine'in accordance with claim 4, the combination with the parts and features therein specified, of a micrometer adjusting mechanism combined with an adjustable stop .mechanism whereby the wheel slide may be moved to an inoperative position through an indefinite distance, said mechanism being arranged so that the wheel slide advance may be stopped at the desired and predetermined position on the next infeeding movement.

6. In a grinding machine having a base, a longitudinally movable work support and a transa transversely movable supporting member on said slide, an angularly adjustable head on said member to support said grinding wheel, said versely movable rotatable grinding wheel, a transversely movable wheel slide on said base, and a wheel feeding mechanism therefor including a nut andscrew, an axiallymovable rotatable hand feeding wheel, a speed reduction unit interposed between the feed wheel and nut and screw mechanism, and a'clutch between said hand wheel and the speed reduction unit which is actuated by'axial movement of said hand wheel, said mechanism and unit being arranged when the clutch is engaged to connect the hand wheel to rotate the feed screw rapidly and whenthe clutch is disengaged to rotate the feed screw slowly.

7. In a grinding machine having a base, a longitudinally movable work support and a transversely movable rotatable grinding wheel, a longitudinally movable work table. including a 'manually operable table traverse mechanism comprising an axially movable rotatable hand traverse wheel, a rack and gear mechanism operatively connected to move said table, a rotat '6 ably mounted speed reduction j unit interposed between the traverse wheel and the rack and gear mechanism; means to hold-said unit against vrotation-whenidesired,iand -a clutchbetween the traverse wheel and :speedreduction unit which is actuated by an axial movement: of said wheel;

said parts being arranged so;that when the clutch is engaged, rotation of the hand wheel serves to rotate the entire unit to produce a relatively fast traversing movement of the table.

7 -8, In-a grinding machine having abase, a 1ongitudinally, movable work support and a trans versely movable-rotatable grinding'wheel; a lon-, gitudinallymovable work table including a manually operable table; traverse mechanism comprising ;an axially movable rotatable hand traverse wheel; a rack and gear mechanism operatively connected to move said table, a rotatably mounted. speed-;reductionj unit interposed be- .tweemthetraverse-wheel and the rackand gear mechanism; means; tojhold said unit against irotatiorr when; desired; and a clutch between the traversewheeland-speed reduction unit which is actuated by' an axial movement of said wheel,

7 said partsbeing arranged so that :when the clutch 10 is; disengaged and; the speed reduction 7 unit held against rotation; a rotary :movementof the hand wheelserves through the-speed reduction unit .to transmit -a relatively slow traversing movement to the table.,

- 'JQH I. GARSIDE. 

